Rotary pump and compressor



NOV' 4 1952 c. J. WLFF 2,616,616

ROTARY PUMP ANO COMPRESSOR Filed Dec. 1e, 1946 2 SHEETS-SHEET 1 CHARLES WOLFF INVENToR. BY Jn l5. @QM/9? ATTORNE YS v Nov. 4, 1952 c. J. woLr-'F 2,616,616

ROTARY PUMP AND COMPRESSOR Filed Dec. 16, 1946 2 SHEETS-SHEET 2 INVENTOR. CHARLEs J.' woLFF BY uFaMSQQM/ve Patented Nov. 4, 1952 UNITED STATES PATENT OFFICE ROTARY PUMP AND COMPRESSOR Charles J. Wolff, San Antonio, Tex.

Application December 16, 1946, Serial No. 716,611

11 Claims. (Cl. 5230-207) The invention relates to a rotary mechanism for the compression of vapors and gases.

An object of the invention is the provision of a compression unit for gaseous iluids which obtains high compression 'eciency Another object ofthe invention is the provision of a compressor in which the pressure differential between the high and low pressure sides of the compressor will serve to actuate a lubricating system for the compressor. This feature obviates the necessity of independent lubricating systems, with their frequent breakdowns and, being governed by the pressure differential on opposite sides of the compressor, will automatically provide greater lubrication when the compressor is laboring under high pressure differentials than when pressure differences are low which is as it should be since greater heat is generated with the high pressure differentials and a greater supply of lubricant is required for ecient operation of the compressor.

Another object of the invention is to provide a means of separating the lubricant from the compressed medium.

A further object of the invention is to obviate the condensation of the medium compressed in the lubricant which condensation normally results in low operating eiliciency and improper lubrication of the compressor.

Another object of the invention is to provide a rotary mechanism adapted to receive and discharge a quantity of uid.

Another obiect of the invention is to provide a rotary mechanism adapted to receive and discharge a Quantity of uid, and having a lubricating system operable as a function of the differential pressure between the receiving and discharge sides of the compressor.

A further object of the invention is to provide in combination, a rotary compressor, a lubricating system therefor, and separator means to separate the lubricant from the medium compressed.

It is a further object of the invention to provide a unit which is readily convertible from a compressor or vacuum pump to a pump for liquids with a minimum of alterations and changeover parts.

Other objects and advantages of the present invention will become apparent with a consideration of the following description and drawings wherein:

Fig. 1 is a vertical cross sectional view of an embodiment of the compressor, partly in elevation, taken on the line I-I of Fig. 2;

Fig. 2 is a vertical cross sectional view, partly.

in elevation, taken on the line 2-2 of Fig. 1;

Fig. 3 is a sectional view, partly in elevation, taken on the line 3--3 of Fig. 2;

Fig. 4.- is an'enlarged fragmentary sectional view of the compressor discharge valve means and the sealing means between the high and the low sides of the compressor being a fragmentary portion of the View shown in Fig. 1;

Fig. 5 is an enlarged isometric view of the sealing bushing between the inlet and outlet conduits of the compressor as the bushing appears when removed from the compressor.

In describing the construction of the invention, attention is invited to Figs. 1 and 2 wherein it will be observed that a compressor assembly denoted as I is shown as comprising a cylindrical member I provided with a central bore 2 and an oiiset bore 3 disposed in parallel relation thereto, and communicating therewith through a slot 4. Secured to each end of the cylinder I are the sealing plates 5 held in position by suitable means such as the screws 6. Adjacent the sealing plates 5 and secured to each end of the cylinder I by suitable means such as the screws 1 which pass entirely through the cylinder member from end to end, are the bearing plates 8 which form the support means for the bearings 9. An eccentric shaft, generally denoted by the numeral I0, is supported by the bearings 9 and is provided on its eccentric portion II with suitable bearings I2 which t the concentric bores of a cylindrical piston element I3 in which the eccentric shaft I6 is free to rotate. A dome I4 which is clamped against one of the bearing plates 3 is held in engagement therewith by means of the screws I which secure the bearing plates to the ends of the cylinder I. in engagement with the other bearing plate by suitable means such as the cap screws I6. The dome I5 is provided at its outer end with a bore and suitable sealing means, which will be described later, through which the driving end of the eccentric shaft I0 passes.

One side of the piston element I3 is provided with an axially extending groove I1 into which is slidably tted a key element I8 passing through the slot 4 and having formed at its outer extremity a cylindrical portion I 9. The cylindrical portion I9 is mounted for oscillating movement in the bore of a bushing 20 which is located in the bore 3 of the cylindrical member I. The bushing 20 is held against rotation and rmly against the outer wall of the bore 3 by means such as the cap screws 2| threaded through the member I and into the bushing.

Thus, it will be seen that the key element I8 is free to oscillate in the slot I which in turn A second dome I5 is similarly heldoscillates the cylindrical portion I9 thereof in the bushing 2l! in response to the gyratory motion of the piston element I3 caused by rotation of the eccentric shaft I3. The cylinder I, the piston I3, the key element I3, and the bushing 2G are all the same length so that when the sealing plates 5 are in position leakage of fluid around their ends is lessened.

Referring to Figs. 4 and 5 it will be noticed that the bushing 20 is provided along one side with a longitudinal slot 4 which when the bushing is in assembled position coincides with the slot 4 between the bores 2 and 3. A cut recessed portion 22 extending partially around the periphery of the bushing 20 and substantially along' its length serves as a means for establishing communication between the slot 4 and the fluid passages 23 and 24 respectively on opposite sidesiof the key element I3 and the bushing 20 in bore 3. y From the vforegoing it is apparent that rotation of the eccentric shaft I in. a counter-- clockwise direction as seen .iniFig., l will .effect a counter-.clockwise:gyration of vthe piston element I3 which :results in .an intake of fluidfrom the uid passage 23. This fluid is carried around the periphery of the piston element I3, the gyratory motion of the piston element serving to compress and discharge it through the slot 4, around the cut recessed portion 22, and into the discharge passage 24.

Located in the passage 24 closely adjacent the bushing 20 is a check valve'25 which is normally held in its seated position in'an outwardly facing chamfer of the passage by the compression spring 26 both'the valve and the spring being held in proper operating position by means of thev valve guide 2'Iy threadedly secured in the outer end of `the passage 24 and provided with a suitable gasket 28A in order to prevent leakage of uid therefrom. A' dischargey passage 29 serves to establish communication between the passage 24 and the -exterior of the compressor.

In order to balance the piston I3 and reduce its weight, a bore 30 therein as shown in Figs. 1 and 2 is provided. A`counterweight 3| is secured to the eccentric shaft Ill', this counterweight being located inside the dome I5 with itscenter of gravity diametrically opposed to theA eccentric I I. The counterweight thus balances the eccentric II and the piston I3. The bore of the dome I5 through which the eccentric shaft I0 passes is provided with a cover plate 32 having a central bore for the passageof the eccentric shaft IG and a finished inside face as sealing means with the seal 33 which rotates with the eccentric shaft I0 and is held in close sliding relation with the finished face vof the cover plate 32 by means of the compression spring 34 interposedk between the seal 33 andthe hub `of thecounterweight.

A driving pulley 35 connected by means of the belt 36 to any suitable power source furnishes the driving means for the: eccentric shaft I D. The spokes 3'I of the pulley 35 are preferably in the form of fan'blades in order to provide air circulation for cooling the compressor while in operation.

From the foregoing descriptionit vwill be observed thatv fromthe seal 33, on the right hand end in Fig. 2., to the bearing pla-te `8 on the left hand end of the cylinder- I the entire compressor isfenclosed with the exception ofthe passages 23 and 24 and the inlet from the coil 48. For this reason it is apparent that no fluids except those passing throughone or theother of the passages 23 or 24` or the ooily 48v can gain entrance or escape from the compressor. This is of particular importance in dealing with the compression of refrigerants. In the compression of refrigerants, in a closed system, it is common knowledge that the high pressure refrigerant should be kept from contact with the lubricant in the reservoir of the compressor in order to prevent condensation of the refrigerant in the lubricant. From an inspection in Figs. 1 and 2 it is obvious that when the eccentric shaft IB is rotating in a counter-clockwise direction, as seen in Fig. 2, the passage 23 will be the intake, or low pressure passage to the compressor, while the passage 24 is the high pressure outlet from the compressor. The dome I4 is always under low pressure while the dome I5, the bearings 9 and I2, and the piston I3 are subject to a pressure which will vary from high to low depending upon operating conditions as will be described.

In operation, the drivingpulley 35 sconnected to a suitable power supply whichservesto rotatetheeccentric shaft I0., The rotationof this shaft causes thepiston element |3A to ,oscil. late in the cylindrical. member. I. The outside surface. of the piston I3 moves tangentially around the inner walll of the cylindrical member I. Since lubricant is present in the cylinder, a traveling fluid seal is formed in the cylinder as the piston moves along the inner wall.

As this fluid seal passes the .inlet port 23, the piston element I3 moves away from the cylindrical member I due to the eccentric movement of shaft II, a void is created adjacent the inlet port.

This void in turn causes a decrease in pressure on the inlet side of the cylinder so as to draw in a quantity of fluid to be compressed. As the piston continues to travel around the cylinder wall, the fluid is caused to travel ahead of the seal. This charge of fluid moves toward the ou-tlet'port 24 and is discharged therethrough.

The dome I4 is provided with a suitable lubricant 52 to the approximate level indicated in Fig. 2 and the gas, or vapor, to be compressed is admitted to the dome I4 through the inlet conduit 38 and enters the upper end of the conduit 40 above the level of the lubricant passing downwardly therethrough and entering the lcylinder I through the passage 23.- In Figs. Zand 3 it will be noted Athat the juncture of the `conduit 40 with the inlet passage 23 is below the surface of the lubricant and that a small metering hole 4I is provided .in a wall of the conduit 40 proximate its lower'extremity. The purpose of this metering hole is to admit a small quantity of lubricant to the interior -of the conduit 40 from where it will be drawn into the inlet passage 23 and subsequently into the interior of the bore 2 of the cylinder I. The lubricant thus radmitted to the cylinder serves as a lubricant and seal for the periphery of the pistonl I3 and any `excess lubricant admitted therethrough will beldisch'ar-ged through the discharge passage 24 into the `discharge conduit 39.

As a matter of practical knowledge, it has been found in practice that this admission of lubricant to the interior of the compressor results in a substantial increase in the operating efficiency of the compressor especially in the compression' of gases or vapors Where slip is a troublesomer factor.

While the admission of lubricant to the interior of the compressor is of advantage from a standpoint of operating efficiency it is obvious thatthe. lubricant discharged through the discharge conduit 39 would soon exhaust the lubricant from the compressor were not some means provided for reclaiming the lubricant so discharged. Referring to Figs. l, 2, and 3, it will be observed that: the discharge conduit 39 leads to an oil saver 42 which consists of lan insulated cylinder sealed lat both ends. Fluids emerging from the conduit 39 enter a screened strainer 49 which permits passage of gaseous portions 'but upon which particles of lubricant in the uid adhere and gravitate downwardly iin-ally dropping off the lower end of the screen into the bottom of the oil saver 42. The lubricant-free gaseous Iportions pass from the oil saver through the conduit 44, andi'n the case of refrigerants, are carried directly to Ia condenser.

This flow of fluid into the oil saver, the separation of lubricant therefrom and passage of lubricant-free iluid to the condenser continues until suilicient lubricant has collected in the bottom of the -oil saver v'to raise the float 45 lowering the valve 4B andr permitting the lubricant from the bottom of the `oil saver to now into the conduit 41. It is to be noted that the level of the float 45 is so located in the oil saver that the oil level inside the cylinder must Ialways be above the lower end of the conduit 41 before the flioat 45 will open ture illustrated in Fig. 2 wherein the central cylindrical element I constitutes a body to which the sealing plates 5, the bearing plates 8, and the domes I4 and I5 are secured.

Y Broadly the invention contemplates a compressor, which, in combination with rthe automatic and continuous lubricating and sealing provi-sions hereinabove described, comprise a unit adaptable to production manufacturing methods which is economical in cost, highly `eiiicient in operation land `easily serviced in the field.

The invention claimed is:

1. A rotary eccentric compressor comprising a compressor assembly, said assembly including, a cylinder, va low pressure oil reservoir at one end of said cylinder, an inlet port for said cylinder, communicating means including lubricant metering means, between said low pressure oil reservoir and said inlet port, an outlet port for said cylinder communicating with the exterior thereof and connecting with separating means for separating y lubricant from the discharged gas, a conduit from leading to the interior of said high pressure oil v reservoir, a conduit from the point of application the valve 46.' Thus, only lubricant can enter the conduit 41 from the oil saver 42.

Since the temperature inside the oil saver is comparatively high, the oil leaving the oil saver in A the conduit will Ialso be at ia high temperature and in order to'cool this lubricant before putt-ing it to -use again, the conduit 41 is formed into a series of coils `IIB about the compressor, the end of such coil being connected into the dome I5. The' lubricant in dome I5 has access to 'the piston I3.,

in cylinder I through the bearings 9 and I2. .Excess lubricant in the cylinder I will be forced' trance of lubricant through the conduit 41 froml the oil saver 42 and this pressure will build up to proximate the pressure in the discharge conduit 39 while the compressor is running and when the compressor stops, the lubricant inside the piston I3 will slip past the ends of the piston and; through the inlet passage 23 to the interior of the dome I4. Infact, as previously stated during the time the compressor is running, there is a continual flow of lubricant from the dome I5 past the ends of the lpi-ston 'I3 to form a sealing means for the ends of the piston.

In order to prevent a hydraulic lock of the key element |78A in the groove -I1 passages 50 estab,- lish-ing communication between the bottom of the groove I1 :and the low pressure side of the cylinder I are provided whereby any lubricant entrapped beneath the key element I8 will -be discharged therethrough.

Particular lattention is invited here to the construction illustrated in Figs. 4 and 5 wherein the arrangement of the bushing 20, the sealing element I8 between the high and low pressure sides of the compressor Vand its pvot bearing I9, the undercut 22 of the bushing communicating with the passages `23 and 24, and the placement of the check valve 25 are shown in detail. Another feature oi. the greatest importance in economical construction and which contributes greatly4 in promoting .'eiciency of operation is the strucof said gas to said low pressure oil reservoir so 1 that oil will be drawn into said compressor assembly as a function of the diierential between said inlet and outlet ports, an eccentric shaft rotatably mounted and extending through said cylinder, a piston on said shaft, said piston being pivotally mounted in said cylinder so that as said eccentric shaft rotates said piston will move in tangential relation to said cylinder to rst create a vacuum therein, such vacuum force serving to draw a gas through said inlet port into said cylinder to be compressed and discharged through said outlet port.

2. A rotary eccentric compressor comprising a compressor assembly, a low pressure reservoir at one end of said assembly, a high pressure oil reservoir at the other end of said assembly, said assembly including a cylinder, an inlet port for said cylinder communicating with said low pressure oil reservoir, an outlet port for said cylinder to the exterior thereof, an eccentric shaft rotatably mounted and extending through said cylinder, a piston on said shaft, said piston being pivotally mounted in said cylinder so that as said eccentric shaft rotates said piston will move in tangential relation to said cylinder to rst create a vacuum, therein, such vacuum force serving to draw a gas through said inlet port into said cylinder to be compressed and discharged through said outlet port, metering means connecting said low pressure reservoir and said inlet port so thaty oil will be drawn into said compressor assembly as a function of the differential pressure between said inletand outlet ports, separate means connected on the outlet side of said compressor to separate the compressed gas from the oil, and conduit means to conduct the separated oil to said high pressure oil reservoir connected on said assembly.

3. In a rotary eccentric-',compressor, a pair of oil reservoirs, a compressor assembly therebetween, said assembly including a cylinder, an inlet port for said cylinder communicating with one of said reservoirs, an outlet port for said cylinder leading `to the exterior thereof, an eccentric shaft rotatablyk mounted extending through said one of said reservoirs and said cylinder, a piston on said shaft, said piston` being pivotally mounted insaid cylinder so thatY as said shaft rotatesv the piston moves in tangential re'- lation to said cylinder so as to first create a vacuum therein, such vacuum force tending to draw a medium in through said inlet port into said cylinder to be compressed and discharged through said outlet port, metering means connecting said one of said reservoirs to said inlet port for lubricating the moving parts cf said compressor assembly as a function of the differential pressure between said inlet and outlet ports, the other of said reservoirs serving as an oil overfiow receptacle.

4. In a rotor compression mechanism adapted to continuously receive a quantity of uuid to be compressed and then discharged therefrom, means to lubrieate and aid in maintaining a seal between the compressing parts of such mechanism, said means being operable automatically as a function of the differential pressure between the .receiving and discharge pressure'of the fluid being compressed, said lubricating means comprising a low pressure lubricant reservoir on the low pressure side of said compressor mechanism, a'

high pressure lubricant reservoir on the high pres-y sure side of said compressor mechanism, a lubricant and gas separating assembly, an inlet port for said compressor mechanism, an outlet port for said compressor mechanism, communicating means between said low pressure lubricant reser- Voir and said inlet port including orice metering means for admitting lubricant to said inlet port, communicating means between said outlet port and said lubricant and gas separating assembly, a conduit from said separating assembly to said high pressure lubricant reservoir, communicating means from said high pressure lubricant reservoir to said compressor mechanism whereby lubricant is admitted to the interior and abutting portions of the compressor mechanism, a conduit from said 1ubricant and gas separating assembly to the point of application of the compressed gas, and a conduit from said low pressure lubricant reser` voir to a source of supply.

5. In a rotary compressor adapted to continu# ously receive a quantity of luid to be compressed and discharged therefrom, a lubricating system for the compressor operable by the pressure differential between the receiving and discharging pressure ci the fluid being compressed so that the compressor will automatically be provided with greater lubrication when the pressure differential is greater, said lubricating means comprising a low pressure lubricant reservoir on the receiving side of said compressor, a high pressure lubricant reservoh` on the discharge side of said compressor, a lubricant and gas separating assembly, an inlet port for said compressor, an outlet port or said compressor communicating vmeans between said low pressure lubricant reservoir and said inlet port including orice metering means for admitting lubricant to said inlet port, communicating means between said outlet port and said lubricant and gas separating assembly,`a conduit from said separating assembly to said high pres-v sure lubricant reservoir, communicating means from said high pressure lubricant reservoir to said compressor whereby lubricant is admitted to the interior and abutting portions of the compressor, a conduit from said lubricant and gas separating assembly to the point of application of the compressed gas, and a conduit from said low pressure lubricant reservoir to a Source of' 8, ou'sly receive a quantity of fluid to be compressed and discharged therefrom, a lubricating system for the compressor operable by the pressure differential between the `receiving and discharge pressure:A of the iluid being compressed so that the' compressor will automatically be provided with' greater lubrication when the pressure differential is greater and so that the amount of lubrication will be decreased when the pressure differential decreases, said lubricating means comprising, a low pressure lubricant reservoir on the receiving side of said compressor, a high pressure lubricant on the discharge Aside of said compressor, a lubricant and gas separating assembly, an inlet port for said compressor an outlet port for said compressor, communicating means between said inlet port and said low pressure reservoir including orice metering means for admitting 'lubricant to 4said inlet port, communicating means between said outlet port and said lubricant and gas separating assembly, a conduitgromsaid separating assembly to said high pressure lubricant-reservoir, communicat-A ing means from said high pressure lubricant reservoir to said compressor whereby lubricant is admitted to the interior `and abutting portions of the compressor, a conduit from said lubricant and gas separating assembly to the point of application of the compressed gas, and a conduit fromvsaid low pressures lubricant reservoir to a source of'supply.v

'7. A rotary mechanism adapted to receive and discharge a. quantity of fluid comprising, a cylinder, 'an inlet port therefor, a low pressure lubricant reservoir on one side of said cylinder in communication with said inlet port, a high pressure lubricant reservoir on the other side of said cylinder, an outlet port for said cylinder leading to the exterior thereof, an eccentric shaft rotatably mounted and extending through said cylinder, a piston moveably mounted in said cylinder so as to move in tangential relation to said cylinder as said shaft rotates, metering means in said inlet port-to furnish lubricant to the moving parts of the mechanism` to form a seal thereof to obviate leakage-of the fluid being compressed from said mechanism, separator means connected to said outlet port to separate the lubricant from the uiddischarged from thc mechanism', float means in said separator means to effect passage of such separated lubricant from said separating means, a conduit from said separator means to said high pressure lubricant reservoir, communicating means between said high pressure lubricant reservoir and the interior of said cylinder, and passage means through the bearings of said cylinder to admit lubricant to the interior -of vsaid cylinder and the abutting ends of said piston and cylinder.

- 8. In' a'compression mechanism adapted to continuously receive .a quantity of uid vto be compressed and discharged therefrom to lubricate theabutting compression mechanism parts of such mechanism, said means being operable as a function 4of the differential pressure between `fthe receiving and discharge pressure vo1' the fluid being compressed, said lubricating means comprising, a low pressure lubricant reservoir located on the inlet side of said compression mechanism and vcommunicating with the inlet port thereof by lconduit means for with.- drawing-low pressure vfluid from said low pressure reservoir, metering means associated withA said conduit below the level of lubricant in said lov;rr.pressure reservoir for: admitting a predeter 'mined amount of lubricant to the fluid being drawn into said compression mechanism, a uid and lubricant separating means with said low pressure lubricant reservoir mechanism leading to the exterior thereof and communicating with said iluid lubricant separating means, ahigh pressure lubricant reservoir on the high pressure side of said compression mechanism, aconduit from said fluid and lubricant separating means to said high pressure lubricant reservoir, communicating means between said high pressure lubricant reservoir and the interior of said compression mechanism, and passage means through the bearings of said compression mechanism whereby high pressure lubricant is admitted to the interior and abutting portions of said compression mechanism.

9. In a rotary compressor adapted to continuously receive a quantity of iluid to be compressed and discharged therefrom, a lubricating system for the abutting compressor parts which is operable as a function of the pressure differential between intake and discharge of the compressor so that the compressor will be automatically provided with greater lubrication when the pressure diierential is greater, said lubricating system comprising a low pressure lubricant reservoir located on the inlet side of said compressor and communicating with the inlet port thereof by conduit means for withdrawing low pressure fluid from said reservoir, metering means associated with said conduit below the level of lubricant in said low pressure for admitting a predetermined amount of lubricant to the fluid being drawn into said compressor, a fluid and lubricant separating means with said low pressure lubricant means, an outlet port for said compressor leading to the exterior thereof and communicating with said fluid and lubricant separating means, a high pressure lubricant reservoir on the high pressure side of said compressor, a conduit from said fluid and lubricant separating means to said high pressure lubricant reservoir, communicating means between said high pressure lubricant reservoir and the interior of said compressor, and passage means through the bearing of said compressor whereby lubricant is admitted to the interior and abutting portions of said compressor.

10. In a rotary compressor adapted to continuously receive a quantity of fluid to be compressed and discharged therefrom, a lubricating system for the abutting parts which is operable as a function of the fluid differential between the intake and discharge pressures of the compressor so that the compressor will be automatically provided with greater lubrication when the pressure differential is greater and so that the amount of lubrication will be decreased when the pressure differential decreases, said lubricating system comprising a low pressure lubricant reservoir located on the inlet side of said compressor and communicating with the inlet port thereof by conduit means for withdrawing low pressure fluid from said reservoir, metering means associated with said conduit below the level of lubricant in said low pressure reservoir for admitting a predetermined amount of lubricant to the fluid being drawn into said compressor, a fluid and lubricant separating means with said low pressure lubricant reservoir, an outlet port for said compressor leading to the exterior thereof and communicating with said uid and lubricant separating means, a high pressure lubricant reservoir on the high pressure side of said reservoir, a conduit from said fluid and lubricant separating means to said high pressure lubricant reservoir, communicating means between said high pressure lubricant reservoir and the interior of said compressor, and passage means through the bearings of said compressor.

l1. A rotary eccentric compressor comprising a hollow cylinder, an eccentric shaft rotatably mounted and extending through said cylinder, means for rotating said shaft, heads for each end of said cylinder, said cylinder having a low pressure end and a high pressure end, a casing forming a lubricant reservoir at the low pressure end of said cylinder, a casing forming a lubricant reservoir at the high pressure end of said cylinder, a piston rotatably on said eccentric shaft said piston being pivotally mounted in said cylinder so that as said eccentric shaft rotates said piston will move in tangential relation to said cylinder, an inlet port on one side of said pivotal mounting, metering means between said inlet port and the interior of said low pressure lubricant reservoir casing beneath the level of the lubricant therein, a conduit from said inlet port metering means to a location above the level of the lubricant in said casing, an inlet port into the upper portion of said casing, an outlet port on the other side of said pivotal mounting, communicating means between said outlet port and the exterior of said cylinder, separator means connected with said outlet port for separating lubricant from the compressed iluid, a conduit from said separating means to the point of application of said compressed fluid, a conduit from said separating means to said low pressure lubricant reservoir casing, all of aforesaid components combining to form a system whereby the periphery of said cylinder and said piston are lubricated by lubricant drawn into the cylinder through the inlet port from the low pressure lubricant reservoir casing, and where the eccentric shaft bearings and abutting ends of said cylinder and said piston are lubricated by lubricant from said lubricant reservoir casing at the high pressure end of said cylinder.

CHARLES J. WOLFF.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 1,566,919 Parkyn Dec. 22, 1925 1,664,733 Braun Apr. 3, 1928 1,768,279 Wood June 24, 1930 2,151,679 Blumer Mar. 28, 1939 2,169,131 Albertson Aug. 8, 1939 2,178,425 Johnson Oct. 31, 1939 2,272,926 Squiller Feb. 10, 1942 2,313,387 McArthur, et al. Mar. 9, 1943 

